Power load equalizer



Feb. 9, 1954 Filed NOV. 29, 1949 E. BERKLEGE POWER LOAD EQUALIZER 5Sheets-Sheet 1 INVENTOR. EM IL BERKLEGE ATTORNEYS Feb. 9, 1954E.'BERKLEGE POWER LOAD EQUALIZER 5 Sheets-Sheet 2 Filed NOV. 29, 1949 INV EN TOR.

EMIL BERKLEGE ATTORNEYS 1954 E. BERKLEGE ,668,459

POWER LOAD EQUALIZER Filed Nov. 29, 1949 5 Sheets-Sheet 4 FIG.- 6

FIG-5 IN V EN TOR. EMIL BERKLEGE ATTORNEYS Feb. 9, 1954 E BERKLEGE I2,668,459

POWER LOAD EQUALIZER Filed NOV. 29, 1949 5 Sheets-Sheet 5 FIG-8 FIG-9 INV EN TOR. EM IL BERKLEGE ATTORN EYS Patented Feb. 9, 1954 UNITED STATESPATENT OFFICE POWER LOAD EQUALIZER Emil Berklege, Cleveland Heights,Ohio Application November 29, 1949, Serial No. 129,992

18 Claims. 1

The invention relates to novel and improvedv devices for thetransmission of power, supplied in the form of rotary motion, from adriving member to a driven member.

An object of the present invention is to provide means for thetransmission of power as aforesaid in such manner as to produce. an.infinitely variable torque, automatically controlled in response to therequirements of the load or in response to the variations in power inthe input.

A further object of the invention is to transmit power as aforesaidthrough mechanical media the elements of which include reduction gearingin operative association with additional means for transmittinginfinitely variable torque.

A further object of the invention is to transmit power as aforesaid bymeans of operatively associated elements capable of relativedisplacement responsive to load variations whereby to achieve aninfinitely variable torque instantaneously responsive to variations inload conditions, but normally tending to produce a one-toone ratiobetween the rotary movement of the driving and driven members.

A further object of the invention is to provide power transmission meansof the character indicated and wherein initial increments of powerapplication are cushioned by the intervention of resilient linkagebetween the input driving means and the output driving means.

A further object is to provide an automaticallyoperated variable torquetransmission in combination with an automatically operated, infinitelyvariable reduction drive.

A further object of the invention is to provide' a transmission of powercharacterized by the absence of steps or jerks as a result of aperfectly smooth acceleration or deceleration response of the drivenshaft.

A further object of the invention is'to provide a transmission asdefined in the last preceding paragraph, and wherein means is providedvfor manual modification of the driving effect, both as to the reductiondrive and the relative direction of rotation as between the driving anddriven shafts;

A further object of the invention is to provide an automatically varyingtorque transmission, and means in operative association therewith forrotating the driven member in counter rotation relationship to thedriving member.

A further object of the invention is to provide transmission means ofthe character defined in any of the preceding paragraphs'which is'simple2 and economical to manufacture and which requires a minimum ofmechanical skill to assemble, install, and maintain in operation.

A further object of the invention is to provide an extremely compactassembly of the elements of the transmission, so that there is no wastedspace or unnecessary bulk.

Other objects and advantages of the invention will be apparent from astudy of the following description of several embodiments of theinvention, in conjunction with the accompanying drawings, in which:

Fig. 1 is a vertical sectional view taken centrally through oneembodiment of my transmission substantially on the axis of rotation ofthe Fig. 7, the parts being in a somewhat different working position;

Fig. 9 is a sectional view taken on the line 9-9 of Fig. 7; and

Fig. 10 is a longitudinal sectional view through another embodiment ofmy invention.

Referring now to the embodiment of the invention shown in Fig. 1, thereis illustrated a stationary housing 20 closed at one end by an integralcontinuation 2| of the side wall. The end wall 21 is provided with aboss 22 which has a' centrally bored cap 23. At its other end thehousing is closed by a plate 24 which is likewise provided with an axialaperture in which is a bushing 25. A drive shaft 26 enters throughbushing 25, and'a driven shaft 2'! extends outwardly through cap 23, thedrive shaft and driven shaft being in axial alignment. The driven shaft21 is integral with a drum 28 within housing 20, and having workingclearance therefrom. A bearing 29 is disposed in the end wall of drum2'8, and the inner end of driving shaft 26 rests in bearing 29. Thedriven shaft is journaled in bearing 30 in boss 2-2.

The open end of drum 28 carries an internal ring gear 33. Driving shaft26 has fixed thereto, or integral therewith, a sun. gear 34 in mesh witha spaced series of planet gears 35 which in turn engage the ring 33. 7

Each planetary gear is fixed on a respective shaft which is journaled,fore and aft, in bushings 31, 38 which are supported in a carrier 39.One end of said carrier is rotatable on a bearing 43 on shaft 28 and theother end on a bushing 44 rotatable on a hub 45, also on shaft 26.Between hub 45 and shaft 26 is a liner or bushing 45. The shaft 36 whichcarries planetary gear 35, has integral therewith a pinion 41 which isin mesh with gear teeth on the end 4511 of hub 45. A sleeve 48 haslimited rotative movement onhub 45, as determined by pins 49 fixed insleeve 48, and extending into segmental slots 50 in hub 45.

A clutch ring 53 is fixed in the end wall of hub 28. A spaced series ofpawls 54 (Figs. 1, 2 and 3) are loosely pivotally mounted in the endwall of hub 45 and extend outwardly through notches 55 in sleeve 48 soas to be adapted, during rotation of the hub under certain conditions tomove outwardly and engage in the internal grooves or recesses 55 inclutch ring 53. Such conditions are encountered, for example, when thedriven shaft becomes the driver, as when the load takes over the driveduring deceleration of input power. Such engagement is depicted in Fig.3, whereas in Fig. 2, during clockwise movement of hub 45 with respectto clutch ring 53, the pawls are cammed inwardly so as to clear theinternal teeth 56.

It will be apparent then that on clockwise motion of hub 45 with respectto clutch ring 53 (integral with drum 28 and driven shaft 2'!) the partswill assume the position shown in Fig. 2, whereby such clockwise motionis permitted. It will be further apparent, from a consideration of Fig.3, that counterclockwise movement of hub 45 with respect to ring 53produces an interlock by means of pawls 54 so that hub 45 and ring 53will rotate as a unit. The pawls are urged inwardly by the combinedaction of the clockwise driving rotation of the hub 45, and the limitedloose linkage of the sleeve 48 which lags momentarily in taking up therotation with the hub 45.

A spiral leaf spring 58 of suitable strength to meet the demand imposedthereon is riveted or otherwise secured at its inner end to sleeve 48and at its outer end to drum wall 28.

The operation of the device shown in Figs. 1, 2 and 3 is as follows.eratively engages a load, and must be turned to overcome the inertia ofthe load. A rotary driv ing force, whether originating from steam,electricity, an internal combustion engine, or otherwise, is applied toshaft 26. Since drum 28 is integral with shaft 21, its tendency is toremain stationary until sufficient torque is developed. Rotation ofshaft 28 rotates sun gear 34 since these parts are integral. Since ringgear 33 is temporarily motionless, and resists initial attempt to moveit, the planet gears 35 rotate on sun gear 34, carrying with them theirshafts 35, pinions 4i, and carrier 39.

Pinions 4! apply to hub 45 a torque which has as its components themeshed engagement between the pinions and the hub, and also the unitaryrotation of the whole carrier 33. At first the only resistance tomovement of the hub is embodied in the coil spring 55, which is sooriented that driving torque tends to wind it from relaxed condition togreater tension. First increments of motion of the hub engages the pins49 with the ends of their respective slots, and sleeve 48 then begins towind the spring imparting leverage through the action of gears 34, 35,

Assume that shaft 21 op- 41, 48 which are arranged in a reduction ratio.Pawls 54 are likewise so oriented that they assume the position shown inFig. 2, whereby they are inactive so far as communicating driving torqueto drum 28 i concerned. When spring 58 is wound a torque is developed,causing such tension as to overcome the resistance of the load, drivingtorque begins to be transmitted to the hub so as to initiate rotation ofshaft 2'1. In steady running the shaft 26 and drum 28 achieve aone-to-one ratio since after the maximum displacement of the parts undera load the parts are automatically adjusted to a condition ofequilibrium, provided there is no change in load or input power. Thespring readjusts itself to normal tension under such conditions.

The arrangement of the pawls 54, Figs. 2 and 3, protects the springconnection should the driven shaft 21 become the driving shaft in suchway as to reverse the direction of relative motion of hub 45 and clutchring 53, whether by the load overrunning or otherwise. In such case thespring 58 is first relaxed, and then the pawls 54, instead of beingcammed out of operative engagement as shown in Fig. 2, are engaged bythe internal gear teeth on clutch ring 53, and the drum and hub 45 willrotate as a unit, thereby preventing injury to the spring.

It will be apparent that sudden increases in driving power will have aneffect similar to inception of driving torque, and will temporarily becushioned and relieved through temporary increase in spring tension.Sudden relief in the driving torque, on the other hand will at firsttend to cause shaft 21 to overrun, relaxing the spring, and initiatingdirect drive between shaft 21 and hub 45 as heretofore explained, untila driven one-to-one ratio is again reached.

The combination of the planetary gearing and the coil spring produces anevenly cushioned torque application which has not heretofore beenachieved, so far as I am aware. By providing reduction gearing ofcharacteristics predetermined to fit the particular adaptation or need,I have secured a working range of increased leverage in the driving endfor overcoming the initial inertia of the load or input powerirregularities.

Figs. 4 to 9 inclusive show a further development of my inventionwherein I have incorporated therewith an automatically effectivereduction drive, and other features new to be described. So far as ispossible the reference characters heretofore applied in Figs. 1 to 3will be applied to identical elements in the succeeding figures. Some ofthe elements, though functioning similarly to some incorporated in thepreceding embodiment, have been changed in shape or otherwise so as tobe adapted to new surroundings, and they will be given new referencecharacters.

In Figs. 4 to 9 the stationary housing 20 is made somewhat larger, butstill has an end wall 2!, and at its other end a plate closure 24. Aninner housing of drum-like form is fixed to the driven shaft 2'! byfasteners 66 which pass through the end wall of the drum into a flange21a of the driven shaft. The inner housing carries the ring gear 33, andthe driving shaft 26 has the now familiar sun gear 34, and the planetarygears 35 are on a supported carrier consisting of a front element 5'!and a rear element 68, in which elements the planetary gear shafts 36are j'ournaled. Carrier parts 61 and 68 are rotatable on shaft 26, but,as will later appean. they may under certain conditions be aces-nae.

5. locked; with respect to closmte: plate: As. in the previousembodiment there. a hub; 45. which.

thereon the sleeve: 4.8 with its pins.- -5.. There is a. spring drum 68-which. in this'embodinot directly connected. to the drivenv shaft, but,as will appean. it is operatively as sociated with the drivenshaft.through gearing to= hereinafter identified.

As; part of this gearing, and in the operative linkage between spring:drum: 68: and. the driven. shaft 21,. there is. a. member, herewithtermed, for'convenience in: reference; a clutch, and consisting of a.pair of. engageable elements: E3 and 14. will be termed clutch plates,contactable: through. a facing member. 15. Clutch plate It isslidablvsplined; to drive shaft 21 at P81, and adapted for limited: movementthercalong; as will appear. Clutch: plate 1a is. keyed to a hub H: whichis: rotatable on shaft- 21'.

As in; the previous embodiment the hub is operatively connected to thespring drum; 69 not only through: the spiing. 58:, and under certainconditions through pawl's 54 engageable with a clutch ring 53.

The. gearing further includes a planetary system comprising: sun gearT81 on spring drum 6 9', and aspaced set of: planet; gears 19 fixedlysupported on. shafts 8n. journaled in bosses 8| in the inner" housingdrum; 85'; Likewise fixedly sup.-

ported on shaft 80'; outside. of drum 55, are pinions i 83' inmesh. witha gear" wheel on hub Tl heretofore mentioned. The meshed engagement, at84 ,.is of longitudinally displaceable character by reason of thehelical character of the engaging teeth, such displacement taking placeunder heavy loading on hub H, as will be more fully explainedhereinaften.

Planetpinions 83 are inmesh with an internal ring gear 85' carriedon adisk: 86-. freely rotatable on hub 1.1;. said. hub havingi releasableengagement with a. second disk 81'. Such engagement will bestbeunderstood. from. a consideration of Figs. t and 6. Segmental pieces 88are pivot-ally pinned near the periphery of disk 86,. in aoircumferential groove 89 therein. and their tip portion is: extend'ableintoan internal peripheral groove in. the: flange 81a of: disk 81. Thecontour of pieces 88 is such. thatv relative rotation between disks. 86and; 81 is permitted in one direction but prevented in. the otherdirection. A

for the: reception of circular plates 90: rotatable on. shafts 80 Thepurpose of the circular plates 90:is;t o; maintain the disk18fi2 inassembled alignment on the hub. 11.

A peripheral shoulder 93 is provided in the stationary housing wall 20':which is complementary to a rabbeted annular groove 9 I in the peripheryof disk 81.

The rotary; drive of shaft 26' and gear 34' is transmitted through thecombined action of members 35, 41,, B5, and as producing increasedleverage and imparting it to. spring 58. The driving. eifect. thusdeveloped. is ultimately transmitted tothe driven shaft 2 the. forcesbeing. simultaneously distributed through the associ ated rotatableparts. Itshould; be borne in mind that the initial: driving effort isconcentrated upon driven member- 21: at. the hubs 81 of the rotaryhousing. 6.5; This concentrationis produced through the rigidityof gears18, 119:, 83,. 8.4,. 3.5 because'oi the frictional grip of members 13',14..

Means: is provided; in the: f 011m of a. sliding. bar

91, the end of which normally engages recesses.

dished. portion of. disk. 86 has an inwardly'opening groove ea in the meor flange m, for normally ma holdishaft-Z] and drum 65 againstnormaldriving efiortz. The spring 58. will. then exert greater eifortthrough. the leverage resulting from gearaction as: previouslydescribed. to turn spring. drum. 69 and produce consequent rotation ofsun. gear 158, planet gears [29, shafts and. planet gears 83 effectiveuponhub H. Hub 1-? cannot at the moment rotate by reason of engagement.of clutch disk. 13' with clutch disk l4-,.,wh-icl-1=.lat-

V ten disk issplined. tothe drivenshaft' as. aforesaid. The torque.applied. to hub Ill at'sp'iral teeth.

84a produces movement of hub. 11 to the left. against yielding; spring$1, thereby disengaging the-clutch disks at I51 This permits the hub 17and disk 1:37 to rotate freely, and further permitsplanet. gear 83 torotate, inducing, counter-ro tation of disk. 86. Upon initiation. of;such counter-rotation, segments 88 jam. in: their grooves in fixed diskv8'1, stopping disk andthe result. is that planet gears 83 run aroundwithin ring. gear 85, carrying of course their shafts 80 and drum 65-Which is: integral with the driven shaft, and consequently turning theloaded. shaft. The reason the loaded shaft can now be. turned is thatthe new gear contours: 1:8, 1.9 83,. 85 are freed for rotation under.the stress of heavy loads. Even here the drive is influenced:

by the infinite range of torqnesecurable with this x transmission. Asthe. load is taken. up and the driven shaft. begins to rotate, reliefat'the point 84 tends to permit hub- 1:1 to move to the rightto permitre-engagement of the disks 13, Hi, and resumption of normal drive.

I have provided means for reversing the driven shaft, as follows.Reference has been made to a sliding.- bar' or look bar. 94' which isnormally biased by: a spring 93; towards the right (Fig. 4) The springis: hooked at one end to a projection $9? on the ban. and at its otherend to a pin 1 00: on the housing wall, and the bar slides inboaringblocks. Hi3, and 1114 on said wall. Reference waspreviouslymade tocarrier-part 61" which rotated with drum 65. by reason. of the fact thatshafts 36-- are journaled in. part 61. It isobviousthatii part. 61,.hereinafter termed a front stopdisk; be held with respect to the housing20.. then. shaits 36,. must. maintain; a fixed position-.1 The: bar; Bilis of a length. such that when it. is

moved to the left, its left end interlocks with notches [65 on front;stop disk; 6 while its right end terminates" its engagement with theback stop disk. 81.. Whereas previously the backstop disk was fixed and:the front stop disk rotated... after the bar 94 is shifted to: the leftthe front: stop disk is fixed and the back stopdisk. can ro tate; Undersuch conditions, when the driving shaft 26; is rotated, disk 6''! islocked against tation, and: then: the sun gear rotation attempts toadvance the planetary gear shaft 36*, as" previously; the shaft 35cannot advance because disk 6 is locked, and as a result rotationofplaneta'ry gears 35 produces counter-rotation of ring gear 33; anddrum: $35: which is a reverse rotation, com

municated' directly to driven shaft 21.

Manipulation of sliding bar 94' may be effected as follows. The housingZonesa bored boss Ill-l thereon which carries a shaft 1-08 (Figs. i and-7);. On the inner end of the shaft'isa crank arm I109 thetip of:Whichis'inserted between: two" lugs! i=9; on bar: 94'. On the outer endof shaft :108 is a crank arm H3. It is apparent. that. by. r

rocking'the crank arm system the shaft 94 may be reciprocated asdesired. This feature will be further explained-hereinafter. V

' Means is provided for manually disengaging clutch disks 13 and 14 forthe purpose of putting into effect the reduction drive as previouslydescribed. On the inner end of the housing 20 is a boss I14 (Figs. 4 and9) in which is journaled a stub II which is in alignment with acooperating stub shaft I16 at the opposite side of the housing.Connecting the shafts, and swingable thereon is a roughtly semicircularyoke II1 straddling the hub I I8 of clutch disk 14. At the ends II9 ofthe yoke are fingers carrying rollers I2I which are seated loosely in agroove I22 in hub II8. Swinging movement of the bowed portion of theyoke around the shafts I I5, IIB, applies a leverage through rollers I2| against huh I I8 so as to disengage disk 14 against the bias ofspring 95, and thereby permit the device to go into reduction gearing.

' The yoke H1 and the sliding lock bar 94 are manually controlled by alever I24 fixed on a shaft I25 which is journaled on a boss I26 onhousing 28. On shaft I25, within the housing, are a pair of spaced camsI21 and I28. Cam I21, as will appear, operates lock bar 94, and cam I28operates yoke II1 to retract clutch plate 14.

Cam I21 engages a roll I29 on the end of a crank lever I38, which isloosely mounted on shaft II5 previously described Said crank lever I38is operatively connected to crank lever H3 by a link I32. Rotation ofshaft I25 and cam I21 to bring the cam rise against roll I29 swings thetwo cranks and link I32 to the left (Fig. '7) so as to shift shaft 94 tothe left whereby its end enters between the notches on disk 61 and comesto rest in a socket on the closure plate 24 In the meantime cam I28 alsorotates with shaft I25, and its raised cam track contacts a roll I33 onyoke II1 so as to swing the yoke and disengage the clutch disk 14. Therelative orientation of the two cams is arranged in this embodiment sothat the clutch may be disengaged, and so held, without initiatingmovement of the lock bar. Fig. 8 shows the cam position in which cam I28has shifted the yoke sufficiently to disengage the clutch, but cam I21has not yet lifted roll I29 enough to shift the lock lever 94. Controllever I24 may be held in any desired position by any conventional means,not shown, such as by a detent engageable along a segmental trackadjacent the lever.

The embodiment of my invention shown in Fig. will now be brieflydescribed. It is similar to Fig. 1 in a number of structural features,

and specific attention will be directed only to those features whereinit differs from the embodiment of Fig. 1.

I have already fully explained the operation of shaft 26, sun gear 34,planet gears 35, ring gear 33, planet gear carrier 39, sleeve 48, andspring 58. The same reference characters are here retained, since thestructure and function of the parts so identified are identical. Spring58 is riveted or otherwise attached to housing 28, and driving torquetransmitted to spring 58 (in a manner soon to be described) is appliedto housing 28 and thence to driven shaft 21 with which said housing 28is integral. Sleeve 48 and clutch ring 53 are operatively engageable ordisengageable through the pawls 54 (Figs. 2 and 3) dependent uponwhether the driven shaft becomes the driving member, as in overrunning,as previously described.

8 In the embodiments so far described the de-'.' scription of theoperation of the various moving elements has been based on theassumption that driving torque was applied to the drive shaft in onedirection only, namely in such direction: that the spring 58 tends to bewound. In the present embodiment my purpose is to provide means wherebythe advantages of the invention may be attained, while permitting driveof shaft 26 in the opposite direction. I.'

Fig. 10 shows the use of a second spiral leaf spring I35 connected to asleeve I36 at its inner end, and to a drum I31 at its outer end. The:springs I 35 and 58 are coiled and connected in opposite directions,that is to say one of them progresses outwardly clockwise, and the othercounterclockwise, when both are viewed from the same end of the housing28. The utility of a double spring arrangement is for such applicationsas those in which the driving member may also be rotated in the oppositedirection to drive the driven member in a like opposite direction,providing infinitely variable torque in either direction.

Hub I38 is driven from planet gear 41, and transmits driving torquethrough sleeve I36 to the spring I35. Hub I38 also is operatively en-'gageable or disengageable with the clutch teeth of the clutch ring I39through pawls I48 in manner already described in connection with Figs. 2and 3. The rearward reduced continuation of drum I3! forms hub I4I whichdrives sleeve 48.

The pawls I48 and 54 are mounted in opposite orientations so that, forexample, looking fromi the right end of Fig. 10, if the relative rotaryclockwise motion of hub I38 and clutch ring I39 is such as to engagepawls I 48 in' the internal;

teeth of clutch ring I39, then relative rotary clockwise motion of hubMI and gear I53 in the same direction and of the same order is such asto disengage pawls 54.

spring I35, pawls I 48 being disengaged fromclutch ring I39, then pawls54 will engage clutch ring 53 so as to achieve a drive through thespring I35 and later through the planetary gear system 34, 35, 33, toturn drum I31 and shaft" the planetary gear system 34, 35, 33, to turndrum I31 and shaft 28 in the other direction.

In Figs. 1, 4 and 10 I have illustrated power transmission trainswhereby power impulses of: variable character may be evenly andautomatically applied to a load in such manner as to normally achieveequilibrium between the driving shaft and the driven shaft at aone-to-one ratio.

In addition, in Fig. 4, I have illustrated further means forautomatically introducing a reduction gear drive to the powertransmission whenever the load exceeds the normal capacity of thegearing mentioned in the last preceding sentence.

This reduction drive is in the power transmission sequence only as longas the load demand requires it. Further, I have shown means for manuallyintroducing the gear reduction, and

maintaining it in the power transmission sequence for any desiredperiod, whether or not the load would otherwise require it. furthershown means for manually reversing the direction of the driven shaftrelative to the driv- As a result of this structure if a torque appliedto driving shaft 26 in one direction is applied to putting tension on Ifthe torque is applied to shaft 26 in I have accents in'g shaft. havelikewise showm means for accommodating; the. advantages of the: abovecharacterized structures to a driving shaft which can be driven ineither direction.

I 'have fully described the" structures shown. in the drawings. It willbe apparentto-those skilled in the art. that various modifications maybe made in the apparatus without departing; from the scope of? theinvention. The gear reduction shown in Fig. 4 forexample,maybeupredeterminedto satisfactorily meet the demandsof. thework anticipated, by inserting a. gear: train: of

- the proper ratioto-takeover the reductiom drive.

The double spring arrangement. such. as. shown in Fig. may beincorporated in Fig. as; a substitute for the"- single springarrangement. In theembodiment of a transmitter as shown in Fig. 1, thefull benefits: of the characterized features are obtained in the: drive.one: directiorr of rotation. The reversal of the drive: shaft Fig. I,will result in a direct one-to-one reversa-l of the driven shaft 21without. benefit: of the aforesaid features. Similar results. are;obtained in the reversal of the drive: shaft 2ft in the" morecomplextransmitter embodied: in; Fig.

4 Other modifications will occur tozthose skilled inthe art uponconsideration. of. the present specification and drawings.

What I' claim is:

1. Power transmission meansof the character described comprising axiallyaligned driving. and driven shafts, a sun. gear fixed on. said: drivingshaft, aring gear fixed with respect to; said driven shaft and outwardlyfrom. said. sun. gear and in the plane thereof; a plurality of. planetgears surrounding said: sun. gear and in. mesh therewith and; with saidring; gear, and spiral spring means the outer end. thereof being. fixedwithrelation to said ring gear, means for operatively' linking the innerend of. said spring: with said sun gear, and said spring beingdisposedtowards coiling motion during preliminary: application of drivingtorqueto the driving shaft.

2. Power transmission means: of the character defined in claim 1, andwherein complementary clutch parts are provided, means for operativelyconnecting one. such part with; said: drive shaft and other means foroperatively' connecting; the

tension with an annular flange. surrounding. a

portion of said driving shaft. radially outwardly from said sun gear; aring gear fixedon the inner periphery of said flange, a plurality ofplanet gears surrounding said sun gear and. in. mesh therewith and withsaid ring. gear, a spiral spring having the outer end thereof fixed tosaidv flange, means for operatively connecting the innerend of saidspiral spring with said sun gear; said spring being disposed towardscoiling; motion during preliminary application. of driving torque to'thedriving shaft.

4. Power transmission means of the character defined in claim andwherein complementary clutchparts are provided, one such part beingfixed to" move with said drum-like extension, and the other such partbeing movable with the inner 10 end of said spring; said parts beingmutually disengageabl'e during normal forward drive, but beingengageahle to prevent damaging uncoi'ling m'ovementof said'. springduring overrunning of said driven shaft.

5. Power transmission means of the character described comprisingaxially aligned driving and driven shafts, a planet gear shaft spacedradially outwardly from said driving shaft, and parallel thereto; a ringgear spaced radially outwardly from said drivingshaft and beyond saidplanet gear-shaft, a drum fixed to said driven-shaft and to said ringgear, a sungear on said driving shaf-t, a planet gear on saidplanet gearshaft in mesh with said sun gear and. said-ring gear, a hub freely:rotatably mounted on said driving shaft, said hub having peripheral gearteeth near one end thereof; a pinion fixed to said planet gear shaft andin mesh with said peripheral gear teeth, a sleeve mounted and: attachedwith a lost motion connection: to the other end. of said hub, a. spiralspring surrounding said sleeve and havinganlinner end: fixed to saidsleeve and an outer end to said drumso as to be operatively effectiveupon. said driven shaft, said spring being adapted for preliminarycoiling movement responsive to movement of saiddriving: shaft so as. toprogressi vely apply increasing driving torque to move saiddriven shaft,and said sun; gear, planet-gears, and ring gear being likewise adaptedtoprogressively apply increasing driving. torque to move said drivenshaftinstepl'essmanner.

6 Power transmission:- means. of the character defined in claim 5: andwherein complementary clutch parts are provided, means: for operativelyconnecting one such: part with one end of said spring, the other such:part: being fixed to move with the said hub, saidparts being mutuallydisengageable during normalforward drive, but being: engageable toprevent damaging uncoi'ling movement of said spring during overrunningof said driven shaft.

7 Power transmission means of the character described comprising axiallyaligned driving and driven shafts, a planet gear shaft spacedradiallyoutwardly from. said driving. shaft, a. ring gear spaced radiallyoutwardly from said driving shaft and beyond. said planet gear: shaft, asungear on driving. shaft, a planet gear on: said planet gear shaft in.mesh with said sun gear and said ring gear, a hubf-reely rotatablymounted on said driving shaft, said hub having peripheral gear teethnear'one end thereof, a pinion fixed to said planetgear shaftandin meshwith said: peripheral gear teeth, a sleeve. mounted. on said hubandattached to rotate with lost motion thereon, a drum freely mounted: onsaid driving shaft surrounding said: sleeve, said ring gear being fi xedto said drum, a spiral spring having its inner end fixed to=sa-id sleeveand itsouterendfixed to said: drum, said drum being provided with acentral bored extension a sleeve mounted on said extension: and attachedto: rotate with lost motion: thereon, a

second spiral spring having its. inner end fixedto said sleeve means.for operatively connecting the outer end of said second spiral springand the driven shaft, said springs being so disposed that firstsaidspring tends to coil while therespective clutch means on the secondsaidspring prevents uncoil ing' movement thereof, and on motion of thedriving shaft in the other direction the second said spring tends tocoil while the respective clutch means on the first said spring preventsuncoiling movement thereof, each said spring being adapted, duringdriving movement in its respective coiling direction, to progressivelyapply increasing driving torque to move said driven shaft, and said sungear, planet gear, and ring gear being likewise adapted to take up thedrive and progressively apply increasing driving torque to move saiddriven shaft in stepless manner.

8. Power transmission means of the character described comprisingaxially aligned driving and driven shafts, a planet gear shaft spacedradially outward from said driving shaft, and parallel thereto, a ringgear spaced radially outwardly from said driving shaft beyond saidplanet gear shaft and fixed to said driven shaft, a sun gear on saiddriving shaft, a planet gear on said planet gear shaft in mesh with saidsun gear and said ring gear, a hub freely rotatably mounted on said'driving shaft, said hub having peripheral gear teeth near one endthereof, a pinion fixed to said planet gear shaft and in mesh with saidperipheral gear teeth, a sleeve mounted and attached with a lost motionconnection to the other end -of said hub, a spiral spring surroundingsaid sleeve and having an inner end fixed to said sleeve, said springbeing adapted for preliminary coiling movement responsive to movement ofsaid driving shaft, a drum freely rotatable on the driving shaft theouter end of said spring being fixed to said drum, said drum beingprovided with a bored boss having a second sun gear thereon, a

second hub freely rotatable on said driven shaft and having a third sungear thereon, a second planet gear shaft spaced radially outwardly fromthe adjacent ends of said driving and driven shafts and having spacedsecond and third planet gears thereon in mesh respectively with saidsecond and third sun gears, said second planet gear shaft being mountedto revolve in an orbit around and fixed with said driven shaft, a secondatable means is provided for separating said friction members.

10. Power transmission means of the character defined in claim 8, andwherein means is provided for preventing damaging uncoiling movement ofsaid spring during overrunning of said driven shaft.

11. Power transmission means of the character described comprisingaxially aligned driving and driven shafts, a sun gear fixed on saiddriving shaft, a ring gear, means for operatively connecting said ringgear with respect to said driven shaft and outwardly from said sun gear,a plurality of planet gears surrounding said'sun gear and in meshtherewith and with said ring gear, and spiral spring means, the outerend thereof being fixed with relation to said ring gear means foroperatively connecting the inner end of said spring with said sun gear,said spring being disposed towards coiling motion during preliminaryapplication of driving torque to the driving shaft.

12. Power transmission means of the character described comprisingaxially aligned driving and driven shafts, a planet gear shaft spacedradially outward from said driving shaft, and parallel thereto, a ringgear spaced radially outwardly from said driving shaft beyond saidplanet gear shaft and fixed to said driven shaft, a sun gear on saiddriving shaft, a planet gear on said planet gear shaft in mesh with saidsun gear and said ring gear, a hub freely rotatably mounted on saiddriving shaft, said hub having peripheral gear teeth near one endthereof, a pinion fixed to said planet gear shaft and in mesh with saidperipheral gear teeth, a sleeve mounted and attached with lost motion onthe other end of said hub, a spiral spring surrounding said sleeve andhaving an inner end fixed to said sleeve, said spring being adapted forpreliminary coiling movement responsive to movement of said drivingshaft, a drum freely rotatable on the driving shaft the outer end ofsaid spring being fixed to said drum, said drum being provided with abored boss having a second sun gear thereon, a second hub freelyrotatable on said driven shaft and having a third sun gear thereon, asecond planet gear shaft spaced radially outwardly from the adjacentends of said driving and driven shafts and having spaced second andthird planet gears thereon in mesh respectively with said second andthird sun gears, the meshed engagement between said third planet gearand said third sun gear being through spiral gear teeth of the typedisposed towards endwise displacement under heavy load, said secondplanet gear shaft being mounted to revolve in an orbit around and fixedwith said driven shaft, a second internal ring gear in mesh with saidthird planet gears, means for holding said second ring gear stationary,a first friction member fixed on said second hub, a second frictionmember splined on said driven shaft and engageable with said firstfriction member, said friction members being separatable by endwisemovement of said second hub upon application of a heavy load to saidspiral gear teeth as aforesaid.

13. Power transmission means of the type defined in claim 12, whereinspring means is provided eifective upon said second friction member tonormally tend to maintain it in contact with said first friction member,said second member being movable endwise in its splined connection tosaid driven shaft, and manually operatable leverage operativelyengageable with said second friction member against the bias of saidlast named spring means to disengage said first and second frictionmembers when said leverage is operated.

14. Power transmission means of the character described comprising afixed housing, axially aligned driving and driven shafts journaled inopposed walls of said housing and extending therewithin, a planet gearshaft within said housing and spaced radially outwardly from saiddriving shaft, and parallel thereto, a ring gear spaced radiallyoutwardly from said driving shaft beyond said planet gear shaft andfixed to said driven shaft, a sun gear on said driving shaft, a planetgear on said planet gear shaft in mesh with said sun gear and said ringgear, a hub freely rotatably mounted on said driving shaft, said hubhaving peripheral gear teeth near one end thereof, a pinion fixed tosaid planet gear shaft and in mesh with said peripheral gear teeth, asleeve mounted and attached with lost motion on the other end of saidhub, a spiral 13 spring surrounding said sleeve and having an inner endfixed to said sleeve, said spring being adapted for preliminary coilingmovement responsive to movement of said driving shaft, a drum freelyrotatable on the driving shaft, the outer end of said spring being fixedto said drum, said drum being provided with a bored boss having a secondsun gear thereon, a second hub freely rotatable on said driven shaft andhaving a third sun gear thereon, a second planet gear shaft spacedradially outwardly from the adjacent ends of said driving and drivenshafts and having spaced second and third planet gears fixed thereon andin mesh respectively with said second and third sun gears, said secondplanet gear shaft being mounted to revolve in an orbit around and fixedwith respect to said driven shaft, a second internal ring gear in meshwith said third planet gear, a first friction member fixed on saidsecond hub, a second friction member splined on said driven shaft andengageable with said first friction member, a first stop memberrotatable around the driving shaft and having a portion of said firstplanet gear shaft seated therein, a second stop member rotatable aroundthe driven shaft and being fixable with relation to said second internalring gear during movement of said second internal ring gear in onedirection only, and reversing means carried on said housing and adapted,by movement thereof, to prevent rotation of said first stop member whensaid reversing means-is moved in one direction, and to pre vent rotationof said second stop member when said reversing means is moved in theother direction, so as respectively to produce reverse rotation orforward rotation of said driven shaft.

15. Power transmission means of the type defined in claim 14 and whereinspring biasing means is provided normally urging said reversing memberto a position causing forward rotation of said driving shaft.

16. Power transmission means of the type defined in claim 14 and whereinmeans is provided for automatically separating said friction member whenthe load on said driving shaft exceeds a critical value.

17. Power transmission means of the type defined in claim 14 whereinmeans is provided for automatically separating said friction memberswhen the load on said driving shaft exceeds a critical value, andwherein further means is provided for manually separating said membersprior to movement of said reversing member.

18. A planetary reduction gearing comprising axially aligned driving anddriven shafts, a sun gear fixed on said driving shaft, a ring gear fixedwith respect to said driven shaft and outwardly from said sun gear andin the plane thereof, a drum fixed to said driven shaft and to said ringgear, a plurality of planet gear shafts surrounding said sun gear, aplurality of planet gears, each on a respective planet gear shaft, andeach planet gear in mesh simultaneously with said sun gear and with saidring gear, spiral spring means, means for operatively connecting theouter end of said spring means with said drum, other means foroperatively linking the inner end of said spring with said sun gear,said spring being disposed towards coiling motion during preliminaryapplication of driving torque to the driving shaft.

EMIL BERKLEGE.

References Cited in the file of this patent UNITED STATES PATENTS NumberName Date 1,997,503 Wheeler Apr. 9, 1935 2,031,247 Bischof Feb. 18, 1936

